JPS6222667Y2 - - Google Patents
Info
- Publication number
- JPS6222667Y2 JPS6222667Y2 JP1981108394U JP10839481U JPS6222667Y2 JP S6222667 Y2 JPS6222667 Y2 JP S6222667Y2 JP 1981108394 U JP1981108394 U JP 1981108394U JP 10839481 U JP10839481 U JP 10839481U JP S6222667 Y2 JPS6222667 Y2 JP S6222667Y2
- Authority
- JP
- Japan
- Prior art keywords
- friction plate
- piston
- pressure
- pressure accumulation
- chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000009825 accumulation Methods 0.000 claims description 21
- 238000009434 installation Methods 0.000 claims description 8
- 239000003921 oil Substances 0.000 description 21
- 230000007246 mechanism Effects 0.000 description 12
- 239000010720 hydraulic oil Substances 0.000 description 9
- 230000002093 peripheral effect Effects 0.000 description 4
- 238000007789 sealing Methods 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 102100025490 Slit homolog 1 protein Human genes 0.000 description 1
- 101710123186 Slit homolog 1 protein Proteins 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
Landscapes
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Description
【考案の詳細な説明】
本考案はモジユレーシヨン機構を備えた産業機
械、建設機械、農業機械や船舶等の油圧クラツチ
に関する。[Detailed Description of the Invention] The present invention relates to a hydraulic clutch for industrial machinery, construction machinery, agricultural machinery, ships, etc., which is equipped with a modulation mechanism.
この種の機構は前後進切替、速度切替、インチ
ング時等にクラツチを緩やかに接続するためのも
ので、従来この種の機構としてはバルブ式のもの
が主に使用され、又一部ではばね式のものが採用
されている。ところが上記バルブ式の機構では昇
圧式、蓄圧式、絞り可変式、絞り切替式等のバル
ブを油圧回路の途中に設けるようになつているの
で、構造が複雑化し、コストが高くなるという不
具合がある。又ばね式の機構としてはクラツチ内
部に皿ばねを組み入れた構造や、摩擦板をコニカ
ルに成形して弾性を持たせた構造等が採用されて
いるが、いずれの場合でも弾性変形量に限界があ
るので、所望のモジユレーシヨン特性を得にくい
という不具合があり、又摩耗により特性が変化す
るという不具合がある。 This type of mechanism is used to gently connect the clutch during forward/reverse switching, speed switching, inching, etc. Conventionally, valve type mechanisms have been mainly used, and some have spring type mechanisms. have been adopted. However, in the above-mentioned valve type mechanism, a pressure boost type, pressure accumulation type, variable throttle type, or throttle switching type valve is installed in the middle of the hydraulic circuit, which has the disadvantage of complicating the structure and increasing cost. . In addition, spring-type mechanisms include a structure in which a disc spring is incorporated inside the clutch, and a structure in which a friction plate is formed into a conical shape to provide elasticity, but in either case, there is a limit to the amount of elastic deformation. Therefore, there is a problem that it is difficult to obtain the desired modulation characteristics, and there is also a problem that the characteristics change due to wear.
本考案は上記従来の不具合を解決するために、
蓄圧式モジユレーシヨン機構を摩擦板押圧用油圧
ピストンに内蔵させたもので、図面により説明す
ると次の通りである。 In order to solve the above-mentioned conventional problems, this invention
A pressure accumulation type modulation mechanism is built into a hydraulic piston for pressing a friction plate, and the explanation using the drawings is as follows.
断面部分略図である第１図において、１はクラ
ツチ入力軸２の外周側に軸２と一体的に設けたシ
リンダ、３はシリンダ１と軸２の間に嵌合する環
状のピストン、Ｏ−Ｏはクラツチ中心線である。
シリンダ１はピストン３よりも図中右方へ筒状に
延長され、該延長部５には複数の環状摩擦板６
（ドライブプレート）の外周突起が摺動自在に嵌
合するスリツト７が中心線Ｏ−Ｏと平行に設けて
あり、延長部５の先端部内面には摩擦板６の摺動
を阻止するストツパリング９が取り付けてある。
隣接する各２枚の摩擦板６，６の間にはそれぞれ
環状の摩擦板１０（ドリブンプレート）が配置さ
れ、摩擦板１０の内周に設けた突起は筒状出力軸
１１に形成した中心線Ｏ−Ｏと平行なスリツト１
２に摺動自在に嵌合している。出力軸１１と入力
軸２の間には圧縮コイルスプリング１３が配置さ
れ、スプリング１３の図中左端はピストン３の内
周部に圧接し、図中右端は入力軸２上に取り付け
た環状のスプリングシート１４に圧接している。
ピストン３の背面（摩擦板６と反対側の端面）と
シリンダ１の端壁との間に形成された加圧室１５
は入力軸２の内部に設けた油路１８、ならびに手
動切替弁１６や絞り１７を有する外部油路１９を
介して油圧ポンプ２０に接続している。ポンプ２
０は例えばフオークリフトの走行用エンジン（図
示せず）で駆動されるようになつている。 In FIG. 1, which is a schematic partial cross-sectional view, 1 is a cylinder provided integrally with the shaft 2 on the outer peripheral side of the clutch input shaft 2, 3 is an annular piston fitted between the cylinder 1 and the shaft 2, O-O is the crutch center line.
The cylinder 1 is cylindrically extended from the piston 3 to the right in the figure, and the extended portion 5 includes a plurality of annular friction plates 6.
A slit 7 into which the outer peripheral protrusion of the drive plate (drive plate) is slidably fitted is provided parallel to the center line O-O, and a stopper ring 9 is provided on the inner surface of the tip of the extension 5 to prevent the friction plate 6 from sliding. is installed.
An annular friction plate 10 (driven plate) is arranged between each two adjacent friction plates 6, 6, and a protrusion provided on the inner circumference of the friction plate 10 is aligned with the center line formed on the cylindrical output shaft 11. Slit 1 parallel to O-O
2 is slidably fitted. A compression coil spring 13 is arranged between the output shaft 11 and the input shaft 2. The left end of the spring 13 in the figure is in pressure contact with the inner circumference of the piston 3, and the right end in the figure is an annular spring attached to the input shaft 2. It is in pressure contact with the sheet 14.
A pressurizing chamber 15 is formed between the back surface of the piston 3 (the end surface opposite to the friction plate 6) and the end wall of the cylinder 1.
is connected to the hydraulic pump 20 via an oil passage 18 provided inside the input shaft 2 and an external oil passage 19 having a manual switching valve 16 and a throttle 17. pump 2
0 is designed to be driven by, for example, a forklift driving engine (not shown).
ピストン３の外周寄りの部分には環状の蓄圧室
２３が中心線Ｏ−Ｏと同芯に設けてある。蓄圧室
２３は摩擦板６に近い位置にあり、摩擦板６に向
かつて広く開口している。２１，２２は蓄圧室２
３の外周側開口縁と内周側開口縁を形成するピス
トン３の端部で、これらの端部２１，２２は隣接
する摩擦板６に後述する如く圧接して両者間の隙
間２５，２６を密閉できるようになつている。す
なわち端部２１，２２により摩擦板６，１０の設
置空間２８に対して蓄圧室２３を閉塞できる密閉
機構が形成されている。ピストン３の内部には中
心線Ｏ−Ｏと平行な１本又は複数本の絞り油路２
７が設けてあり、油路２７を介して蓄圧室２３は
加圧室１５に連通している。 An annular pressure accumulation chamber 23 is provided in a portion near the outer periphery of the piston 3 so as to be coaxial with the center line OO. The pressure accumulating chamber 23 is located close to the friction plate 6 and has a wide opening toward the friction plate 6. 21 and 22 are pressure accumulation chamber 2
These end portions 21 and 22 of the piston 3 form the outer peripheral opening edge and the inner peripheral opening edge of the piston 3, and these end portions 21 and 22 are pressed into contact with the adjacent friction plate 6 as described later to close the gaps 25 and 26 between them. It is designed to be sealed tightly. That is, the ends 21 and 22 form a sealing mechanism that can close off the pressure accumulation chamber 23 with respect to the installation space 28 of the friction plates 6 and 10. Inside the piston 3, there is one or more throttle oil passages 2 parallel to the center line O-O.
7 is provided, and the pressure accumulation chamber 23 communicates with the pressurization chamber 15 via an oil passage 27.
上記摩擦板設置空間２８は、各摩擦板６，１０
の軸方向（第１図で左右方向）両側ならびに内周
側及び外周側に形成される空間であり、該空間２
８にはドレン油路４０の入口が接続している。 The friction plate installation space 28 includes each friction plate 6, 10.
A space formed on both sides in the axial direction (left and right direction in Figure 1) and on the inner and outer circumferential sides of the space 2.
8 is connected to the inlet of a drain oil passage 40.
クラツチを接続する場合には、切替弁１６を接
続方向に切り替え、ポンプ２０から油路１９，１
８を介して加圧室１５へ作動油を導入する。そう
すると第２図の如くクラツチ油圧Ｐ（加圧室１５
内の油圧）は短時間（０〜T1）で比較的小さい所
定圧P1まで上昇し、ピストン３は速やかに摩擦板
６側へ移動し始める。この初期の移動により端部
２１，２２が摩擦板６を押し、各摩擦板６，１０
は互に圧接を開始してクラツチは半クラツチ行程
の初期の状態となつて接続され始める。 When connecting the clutch, the switching valve 16 is switched to the connecting direction, and the oil passages 19, 1 from the pump 20 are
Hydraulic oil is introduced into the pressurizing chamber 15 via 8. Then, as shown in Fig. 2, the clutch oil pressure P (pressure chamber 15
The internal hydraulic pressure increases to a relatively small predetermined pressure P 1 in a short period of time (0 to T 1 ), and the piston 3 immediately begins to move toward the friction plate 6 side. This initial movement causes the ends 21 and 22 to push the friction plates 6, causing each friction plate 6 and 10 to
The clutches begin to press against each other, and the clutch becomes connected in the initial state of the half-clutch stroke.
半クラツチ行程（第２図のM1〜M2）において
は、加圧室１５内の作動油の一部が絞り油路２７
を通つて蓄圧室２３へ流出するので、油圧Ｐは緩
やかに上昇する。又摩擦板６に対する端部２１，
２２の圧接力が比較的弱く、隙間２５，２６は不
完全な状態で閉鎖されているので、隙間２５，２
６は絞り通路を形成しており、従つて蓄圧室２３
内の作動油の一部は不完全に閉鎖された隙間２
５，２６を通つて摩擦板設置空間２８へ流出し、
この点においても油圧Ｐは緩やかに上昇する。し
かも摩擦板６に対する端部２１，２２の圧接力は
次第に上昇するので、隙間２５，２６を通つて流
出する作動油の量は次第に減少し、従つて半クラ
ツチ行程の終り（M2）に近付くにつれて油圧上昇
率（（勾配）は次第に上昇する。このように半ク
ラツチ行程M1〜M2ではクラツチ油圧Ｐが前記値
P1からそれよりもやや高い油圧P2まで緩やかに上
昇するので、ピストン３から摩擦板６，１０に加
わる押圧力は緩やかに増加し、半クラツチ状態に
あるクラツチはシヨツクを発生することなく滑ら
かに接続する。 During the half-clutch stroke (M 1 to M 2 in FIG. 2), a portion of the hydraulic oil in the pressurizing chamber 15 flows into the throttle oil passage 27.
Since the oil flows out to the pressure accumulation chamber 23 through the air, the oil pressure P gradually increases. Also, the end portion 21 for the friction plate 6,
22 is relatively weak and gaps 25 and 26 are incompletely closed, gaps 25 and 2
6 forms a throttle passage, and therefore the pressure accumulation chamber 23
Some of the hydraulic fluid in the gap 2 is incompletely closed.
5, 26 to the friction plate installation space 28,
At this point as well, the oil pressure P gradually increases. Moreover, since the pressing force of the ends 21 and 22 against the friction plate 6 gradually increases, the amount of hydraulic oil flowing out through the gaps 25 and 26 gradually decreases, and therefore approaches the end of the half-clutch stroke (M 2 ). The oil pressure increase rate ((gradient) gradually increases as
Since the oil pressure gradually increases from P 1 to P 2 , which is slightly higher than P 1, the pressing force applied from the piston 3 to the friction plates 6 and 10 increases gradually, and the clutch in the half-clutch state smoothly moves without causing shock. Connect to.
油圧Ｐが所定値P2となつて半クラツチ行程M1
〜M2が終了した時点（T2）では、蓄圧室２３に作
動油が充満し、又隙間２５，２６は完全に閉鎖さ
れて蓄圧室２３内の作動油が空間２８へ流出でき
ない状態となつているので、それ以後は加圧室１
５から蓄圧室２３へ作動油が流出することはな
い。従つて加圧室１５は急激に加圧され、ピスト
ン３は速やかに摩擦板６，１０を完全接続状態に
なるまで押圧する。従つて半クラツチ状態終了後
（T2〜T3）に摩擦板６，１０間に摩耗の原因とな
る無駄な滑りは生じない。 When the oil pressure P reaches the predetermined value P2 , the half-clutch stroke M1
~ At the end of M 2 (T 2 ), the pressure accumulation chamber 23 is filled with hydraulic oil, and the gaps 25 and 26 are completely closed, so that the hydraulic oil in the pressure accumulation chamber 23 cannot flow out into the space 28. Therefore, after that, pressurization chamber 1
Hydraulic oil does not leak from 5 to the pressure accumulation chamber 23. Therefore, the pressurizing chamber 15 is rapidly pressurized, and the piston 3 quickly presses the friction plates 6 and 10 until they are fully connected. Therefore, after the half-clutch state ends (T 2 -T 3 ), unnecessary slippage that causes wear does not occur between the friction plates 6 and 10.
クラツチを遮断する場合には、切替弁１６を逆
方向に切り替え、加圧室１５内の作動油を油路１
８，１９を介して切替弁１６から排油油路（図示
せず）へ速やかに逃がし、スプリング１３の弾力
によりピストン３を加圧室１５側へ押し戻してピ
ストン３、摩擦板６，１０間の押圧力を解放させ
る。そうすると端部２１，２２と摩擦板６の間に
広い隙間２５，２６が形成されるので、蓄圧室２
３内の作動油が隙間２５，２６を通つて空間２８
へ流出し、蓄圧室２３が空になつて次のクラツチ
接続操作を行える状態となる。なお空間２８へ流
入した作動油はドレン油路４０へ排出されるよう
になつている。 When the clutch is to be disengaged, the changeover valve 16 is switched in the reverse direction, and the hydraulic oil in the pressurized chamber 15 is fed to the oil passage 1.
The oil is then quickly released from the switching valve 16 to a drain oil passage (not shown) via the oil passages 8 and 19, and the piston 3 is pushed back toward the pressurized chamber 15 by the elastic force of the spring 13, releasing the pressing force between the piston 3 and the friction plates 6 and 10. Then, wide gaps 25 and 26 are formed between the ends 21 and 22 and the friction plates 6, so that the pressure in the accumulator chamber 2 is reduced.
The hydraulic oil in the space 3 flows through the gaps 25 and 26 into the space 28.
The hydraulic oil that has flowed into the space 28 is discharged to the drain oil passage 40, and the accumulator chamber 23 becomes empty, so that the next clutch engagement operation can be performed.
以上説明したように本考案によると、ピストン
３の内部に蓄圧室２３を設け、蓄圧室２３を摩擦
板６側に開口させ、かつ絞り油路２７を介して加
圧室１５に連通させ、ピストン３が摩擦板６に圧
接すると蓄圧室２３が摩擦板設置空間２８に対し
て閉鎖されるようにし、このようにピストン３の
内部にモジユレーシヨン機構を設けたので、従来
のように油圧回路の途中（外部）にバルブ式のモ
ジユレーシヨン機構を設ける場合に比べ、構造を
小形簡単化してコストダウンを図ることができ
る。本考案による機構は蓄圧式（油圧式）である
ので、従来の皿ばね等を利用したものに比べ、充
分に緩やかな油圧上昇特性を得ることができると
共に、摩耗による特性の狂いを防止することがで
き、常にクラツチ接続時のシヨツクを確実に防止
することができる。 As explained above, according to the present invention, the pressure accumulation chamber 23 is provided inside the piston 3, the pressure accumulation chamber 23 is opened to the friction plate 6 side, and is communicated with the pressure chamber 15 via the throttle oil passage 27, so that the piston 3 is brought into pressure contact with the friction plate 6, the pressure accumulation chamber 23 is closed to the friction plate installation space 28. Since the modulation mechanism is provided inside the piston 3 in this way, the hydraulic circuit ( Compared to the case where a valve-type modulation mechanism is provided externally, the structure can be made smaller and simpler, and costs can be reduced. Since the mechanism according to the present invention is a pressure accumulating type (hydraulic type), it is possible to obtain a sufficiently gradual hydraulic pressure increase characteristic compared to a conventional mechanism using a disc spring, etc., and it also prevents the characteristics from changing due to wear. This makes it possible to reliably prevent shock when the clutch is engaged.
なおピストン３に蓄圧室２３を設けるには、ピ
ストン３の軸方向寸法を比較的大きく設定する必
要がある。ところが、従来、この種のピストンの
多くは鋳造品で形成されている。そして鋳造品の
場合には、一般に補強リブ等を設ける関係上、そ
の軸方向寸法は大きい。従つて本考案のように蓄
圧室２３を形成しても、ピストン３の寸法が従来
品と比べて大幅に増加することはない。 Note that in order to provide the pressure accumulation chamber 23 in the piston 3, it is necessary to set the axial dimension of the piston 3 to be relatively large. However, conventionally, many of these types of pistons have been formed by casting. In the case of a cast product, its axial dimension is generally large due to the provision of reinforcing ribs and the like. Therefore, even if the pressure accumulating chamber 23 is formed as in the present invention, the dimensions of the piston 3 will not increase significantly compared to conventional products.
なお本考案を具体化する場合、蓄圧室２３を１
個又は複数個の例えば略半球状の凹部により形成
することもできる。端部２１，２２の端面に摩擦
板６と圧接する環状凸部を設けることもでき、又
上記凸部をＯリングのようなシール部材で形成す
ることもできる。 In addition, when embodying the present invention, the pressure accumulation chamber 23 is
It can also be formed by one or more, for example, approximately hemispherical recesses. An annular convex portion that comes into pressure contact with the friction plate 6 may be provided on the end faces of the end portions 21 and 22, or the convex portion may be formed of a sealing member such as an O-ring.
第１図は実施例の断面部分略図、第２図はクラ
ツチ油圧特性のグラフである。
３……ピストン、６……摩擦板、１５……加圧
室、２１，２２……ピストン端部、２３……蓄圧
室、２７……絞り油路、２８……摩擦板設置空
間。
FIG. 1 is a schematic cross-sectional view of the embodiment, and FIG. 2 is a graph of clutch hydraulic characteristics. 3... Piston, 6... Friction plate, 15... Pressure chamber, 21, 22... Piston end, 23... Pressure accumulation chamber, 27... Throttle oil passage, 28... Friction plate installation space.
Claims (1)
かつて開口する蓄圧室を設け、蓄圧室の摩擦板側
開口縁を形成するピストンの端部を、該端部が摩
擦板と圧接して蓄圧室を摩擦板設置空間に対して
閉鎖できるように構成し、蓄圧室とピストン背面
側の加圧室とをつなぐ絞り油路をピストン内部に
設け、摩擦板設置空間をドレン油路に連通させた
ことを特徴とする油圧クラツチ。 A pressure accumulation chamber that opens toward the friction plate is provided inside the hydraulic piston for pressing the friction plate, and the end of the piston that forms the opening edge of the pressure accumulation chamber on the friction plate side is pressed against the friction plate to form the pressure accumulation chamber. The friction plate installation space is configured to be closed to the friction plate installation space, and a throttle oil passage connecting the pressure accumulation chamber and the pressurizing chamber on the rear side of the piston is provided inside the piston, and the friction plate installation space is communicated with the drain oil passage. Hydraulic clutch featuring:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10839481U JPS5812720U (en) | 1981-07-20 | 1981-07-20 | hydraulic clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10839481U JPS5812720U (en) | 1981-07-20 | 1981-07-20 | hydraulic clutch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5812720U JPS5812720U (en) | 1983-01-26 |
| JPS6222667Y2 true JPS6222667Y2 (en) | 1987-06-09 |
Family
ID=29902801
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10839481U Granted JPS5812720U (en) | 1981-07-20 | 1981-07-20 | hydraulic clutch |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5812720U (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5352503B2 (en) * | 2010-03-05 | 2013-11-27 | アイシン・エィ・ダブリュ株式会社 | Multi-plate friction engagement device |
-
1981
- 1981-07-20 JP JP10839481U patent/JPS5812720U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5812720U (en) | 1983-01-26 |
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